JPH0314949A - Differential gear with differential limit mechanism - Google Patents

Abstract

PURPOSE:To prevent generation of pressing action to the meshing part between a pinion gear and side gear by performing fastening of frictional clutch by means of pressing operation through an arrangement by which a side gear boss part penetrates a pressure ring to face the inner face of differential case. CONSTITUTION:When rotation drive force is transmitted to a drive pinion gear, this torque is input to a ring gear 19 and transmitted to a differential case 17. The thrust force generated in the axle direction by a control means such as oil pressure is receive, for performing positioning, by part of receiving ring 39, stopper 41 and differential case 17. The thrust force generated in the axle direction of side gear 13 by the meshing of bevel gears of pinion gear 15 and the side gear 13 is received by part of the differential case 17 to perform positioning in the axle direction similarly.

Description

[Detailed Description of the Invention] [Purpose of Defense] (Field of Industrial Application) This invention provides a differential device that allows differential movement between the left and right wheels of a vehicle, and R Ji4 that limits this differential movement. The present invention relates to a differential gear d with a differential limiting mechanism provided.

(Prior Art) As a conventional differential device with a differential limiting mechanism, for example, there is a device shown in FIG. 2 of Japanese Patent Application Laid-open No. 59-194147.

This device includes a rotatably supported differential case, a second shaft supported by the differential case, a rotatable pinion gear supported by the second shaft, and a pair of gears meshing with the pinion gear. It consists of basic elements such as a side gear, a friction clutch plate that is fastened between the side gear and the differential case to control relative rotation between the two, a binion gear that engages with the side gear, and left and right pressure rings. be.

The breather V ring presses the friction clutch plate against the side gear. Therefore, it is rational because it is easy to assemble and the clutch can be fastened by the pressing motion of the breather V ring.

(Problem that Mitsumei is trying to solve) However, in this case, the conventional differential work restriction mechanism
This device has a problem in that the pressing force of the pressure ring reaches the meshing portion of the pinion gear and the side gear, changing the pack lash in this gear meshing.

Therefore, an object of the present invention is to provide a differential device with a differential limiting mechanism that can prevent the pressing action on the meshing portion of the binion gear and the side gear while allowing the II clutch to be engaged by the suppressing action. In order to solve the problem, a differential gear with a differential limiting mechanism according to the present invention has a differential gear that is rotatably supported. the differential case, and the pinion shaft ↑ and foot supported by this differential case.
A rotatable pinion gear supported by the pinion shaft, a pair of side gears meshing with the pinion gear, a clutch provided between the side gears and the differential case, and regulating the relative rotational speed of the two by tightening. The side gear side of the clutch is provided with a receiving member that receives the side gear side of the clutch against the differential case, and a pressure ring that presses the other side of the clutch in cooperation with an operating means from outside the differential case, and a boss portion of the side gear described in B1. This is achieved by a means characterized in that the breather 1 and the ring are penetrated to face the inner surface of the differential case.

(Function) According to this differential device with a differential limiting mechanism of Kaimei, the thrust force generated when the binion gear and the side gear mesh is transmitted to the inner wall of the differential case 17 via the side gear boss that penetrates the pressure ring. Ru. Therefore, the side gear has the effect of being mispositioned in response to the thrust direction force due to the meshing of the pinion gear and the side gear.

The thrust force from the breather 1F ring is transmitted to the clutch plate and roughly received by the receiving member against the differential case.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. FIG. 1(a) is a cross-sectional view of an embodiment of a differential VJ cylinder assembly with a differential limiting mechanism according to the present invention. iJ3 is located at the lower left of the figure, 1 is an input part that receives the operating hydraulic pressure from an actuator (not shown) of the operating means, 3a is a pressure chamber that transmits the hydraulic pressure from the input part 1, and the end plate 12a of the differential carrier 12 and the piston member 3b. Piston member 3b
is prevented from rotating via a positioning pin 23.

The positioning bin 23 is fixed to the end plate 12a. 5
is a sealing means, and 9 is a dust force bar.

In the basic components of the differential shift limiting device, 11 is an axle;
12 is a differential carrier, 13 is a side gear, and 15 is a binary A gear that meshes with the side gear 13. The binary gear 17 fixed to the differential case 17 is rotatably supported by a foot 16. 19 is a ring gear, and 21 is a cover that closes the opening of the differential key 1.

Next, the configuration for transmitting the thrust force of the operation drive means will be briefly described.

25a and 25b are sealing means for partitioning the pressure chamber 3a;
27 is a ball bearing supported by the piston member 3b, 29 is a pressing force transmitting member, and 31 is a spiral lubrication hole formed on the differential case 17 side outside the pressing force transmitting member 29.

Here, 33 is a tapered roller bearing, 35 is a thrust washer, 37a, 37b are clutch plates, 38 is a pressure ring that presses the clutch plates, 39 is a retaining ring, and 41 is a stopper.

FIG. 1(1)) shows the outline of the pressure ring 38, and is a partially enlarged sectional view taken along the line Q--Q in FIG. 1(a). In the figure, the side gear boss portion 13a faces the inner surface of the differential case 17 shown in FIG. 1(C) through a hole 38a passing through the pressure ring 38, with a thrust washer t-35 interposed therebetween.

The thrust force from the pinion gear 15 shown in FIG. 1(a) is transmitted to the side gear 13, and the differential 1l
This will be resisted by Case 17.

FIG. 1(C) is a partially enlarged sectional view showing the characteristic structure of this embodiment. In the figure, 12 is a differential 7 differential carrier, 13 is a side gear, 15 is a binion gear, 17 is a differential case, 17a is a window of the differential 7 differential case, 33 is a tapered roller bearing,
35 is a thrust washer p, 37a and 37b are clutch plates, 39 is a receiving ring, and 41 is a stopper.

Next, the operation of the embodiment will be explained with reference to FIGS. 1(a) and 1(C). When rotational driving force is transmitted from the blower lever ↑7 foot to the drive binion gear, this torque is input to the ring gear 19. The driving torque input to the ring gear 19 is transmitted to the differential case 17. Then, torque is input from the differential case 17 to the pinion shaft 16 and transmitted to the pinion gear 15 fitted to the pinion shaft 16.

Here, hydraulic pressure is applied to the pressure chamber 3a by an operation control means (not shown).
bearing 27 via piston member 3b.
is transmitted to. The thrust force is then transmitted to the suppressing member 29, and the clutch plate 37a is transmitted via the pressure ring 38.
, 37b. Therefore, the clutch plates 37a, 3
7b is fastened, and differential restriction is performed according to the fastening force.

The thrust force applied to the clutch plates 37a and 37b is received by the differential case 17 via the receiving ring 39 and the stopper 41. Therefore, there is no influence on the backlash of the engagement between the binion gear 15 and the side gear 13, and smooth differential movement can be achieved.

On the other hand, the meshing thrust force between the pinion gear 15 and the side gear 13 is received by the differential case 17 via the thrust washer 35, allowing for reliable positioning, and the NA control is used to prevent it from acting as a fastening force on the clutch plates 37a and 37b. can.

As explained above, the thrust force in the axle direction exerted by the operating means such as hydraulic pressure is stopped by the receiving ring 39, the stopper 41, and the differential case 17, and is stopped by the gear engagement between the pinion gear 15 and the nide gear 13. The thrust force in the axle direction of the side gear 13 generated by
・Received by Lucus 17.

FIG. 2 shows a differential limiting mechanism A-1 according to an embodiment of the present invention.
FIG. 2 is a diagram schematically showing how a limited slip gear is applied to a personal vehicle.

In the figure, 51 is the engine, 52.53 is the front wheel, and 55
is a transmission, 57 is a universal joint, 59 is a propeller shaft, 61 is a universal joint, 63 is a differential device with a differential limiting mechanism according to an embodiment of the present invention,
64.65 is the rear wheel.

Here, the driving rotational force from the engine 51 passes through the transmission 55, the universal joint 57, the blower shaft 59, and the universal joint 61. It is distributed to the rear wheels 64,65 by a single differential 63.

[Advantageous Effects of the Invention 1] As explained above, according to Mitsume's differential device with a differential limiting mechanism, the thrust force in the axle direction due to the bevel gear meshing of the binion gear and the side gear is received by a part of the differential case. Positioning is done. At the same time, the thrust force in the axle direction from an operating means such as hydraulic pressure is received by the receiving member and a part of the differential case, and the positioning member is similarly positioned in the axle direction.

Therefore, the differential device with a differential limiting mechanism of the present invention has the effect of stabilizing meshing backlash between the pinion gear and the side gear.

[Brief explanation of drawings]

FIG. 1(a) is a sectional view showing an embodiment of a differential device with a differential limiting mechanism of the present invention, and FIG.
), FIG. 1(C) is a partially enlarged sectional view showing the characteristic configuration of the embodiment of the present invention, and FIG. 2 is a differential restriction of the embodiment of the present invention. FIG. 1 is a schematic diagram showing an example of an application of a mechanical differential device to an automobile. 11... Axle 13... Side gear 15... Pinion gear 17... Differential case 37a, 37b... Clutch plate 38... Pressure ring 39... Retaining ring (receiving member) 41 ...Stopper 63...Differential shift device with differential shift restriction mechanism

Claims (1)

[Claims] A differential case that is rotatably supported, a pinion shaft that is supported by the differential case, a rotatable pinion gear that is supported by the pinion shaft, a pair of side gears that mesh with the pinion gear, and the side gear and the differential case. a clutch that is provided between the differential case and the clutch that regulates the relative rotational speed between the two when fastened; a receiving member that receives the side gear side of the clutch against the differential case; and a clutch that is connected to an operating means from outside the differential case and that 1. A differential gear with a differential limiting mechanism, comprising a pressure ring capable of pressing the other side, and a boss portion of the side gear passes through the pressure ring and faces an inner surface of a differential case.